Lubrication system for an automatic transmission having dual input shafts

ABSTRACT

A lubrication system is provided for a transmission including a lubrication pump driven by a reverse idler gear. The lubrication pump is supported by a partition plate having an inlet passage and an outlet passage formed therein for communicating with the lubrication pump. The outlet passage communicates with an input shaft extending through the partition plate for supplying lubrication fluid to a central passage in the input shaft.

BACKGROUND OF THE INVENTION Field of the Invention

The present invention relates to an automatic transmission, and moreparticularly, a lubrication system for an automatic transmission havingdual input shafts.

BACKGROUND AND SUMMARY OF THE INVENTION

There are presently two typical power transmissions in use on theconventional automobile. The first, and oldest, type of powertrain isthe manually operated powertrain. These powertrains are typicallycharacterized in that vehicles having manual transmissions include aclutch pedal to the left of a brake pedal and a gear shift lever whichis usually mounted at the center of the vehicle just behind thedashboard. To operate the manual transmission, the driver mustcoordinate depression of the clutch and accelerator pedals with theposition of the shift lever in order to select the desired gear. Properoperation of a manual transmission is well known to those skilled in theart, and will not be described further herein.

In a vehicle having an automatic transmission, no clutch pedal isnecessary. The standard H configuration of the shift lever is replacedby a shift lever which typically moves back and forth. The driver needonly select between park, reverse, neutral, drive, and one or two lowgears. As is commonly known in the art, the shift lever is placed in oneof several positions having the designator P, R, N, D, 2, and maybe 1which corresponds to Park, Reverse, Neutral, Drive, and one or two lowgears, respectively. Vehicle operation when the gear shift lever isplaced in one of these positions in well known in the art. Inparticular, when in the drive mode, the transmission automaticallyselects between the available forward gears. As is well known, oldersystems typically included first, second and third gears, while newersystems include first through third gears as well as fourth and possiblya fifth and sixth overdrive gear. The overdrive gears provide animproved fuel economy at higher speeds.

As is well known, early transmissions were almost exclusively manuallyoperated transmissions. With a steady development of automatictransmissions, drivers increasingly gravitated toward the easy operationof automatic transmissions. However, in the mid 1970s, rising concernsabout present and future fossil fuel shortages resulted in animplementation of corporation average fuel economy regulationspropagated in several countries. These fuel economy requirementsnecessitated the investigation of increasing the fuel economy of motorvehicles in order to meet government regulations. These governmentregulations prompted a gradual return to manual transmissions which aretypically more efficient than automatic transmissions.

In the ensuing years, many mechanically operated vehicle systems werereplaced or at least controlled by electronic control systems. Theseelectronic control systems greatly increased the fuel efficiency ofvehicle engines and enabled a gradual return to the convenience ofautomatic transmissions. In addition, electronic controls used withautomatic transmissions, greatly improved the shift schedule and shiftfeel of automatic transmissions and also enabled implementation offourth and fifth overdrive gears thereby increasing fuel economy. Thus,automatic transmissions have once again become increasingly popular.

Automatic and manual transmission offer various competing advantages anddisadvantages. As mentioned previously, a primary advantage of a manualtransmission is improved fuel economy. Conversely, automatictransmissions first and foremost offer easy operation, so that thedriver need not burden both hands, one for the steering wheel and onefor the gear shifter, and both feet, one for the clutch and one for theaccelerator and brake pedal, while driving. When operating a automatictransmission, the driver has both one hand and one foot free. Inaddition, an automatic transmission provides extreme convenience in stopand go situations, as the driver need not worry about continuouslyshifting gears to adjust to the ever-changing speed of traffic.

The primary reason for the superior efficiency of the manualtransmission over the automatic transmission lies in the basic operationof the automatic transmission. In most automatic transmissions, theoutput of the engine connects to the input of the transmission through atorque converter. Most torque converters have an input turbine that isconnected to the output shaft of the engine and an input impeller thatis connected to the input shaft of the transmission. Movement of theturbine at the input side results in a hydraulic fluid flow which causesa corresponding movement of the hydraulic impeller connected to theinput shaft of the transmission. While torque converters provide asmooth coupling between the engine and the transmission, the slippage ofthe torque converter results in a parasitic loss, thereby decreasing theefficiency of the powertrain. Further, the shift operation in anautomatic transmission requires a hydraulic pump which pressurizes afluid for clutch engagement. The power required to pressurize the fluidintroduces additional parasitic losses of efficiency in the powertrain.

Before a shift between the gear ratios of a manual transmission canoccur, it is necessary to synchronize the rotational speed of thedriveshaft with the rotational speed of the driven shaft. Typically,synchronization is obtained in a manual transmission by way of asynchronizing mechanism such as a mechanical synchronizer which is wellknown in the art. The mechanical synchronizer varies the speed of thedriveshaft to match the speed of the driven shaft to enable smoothengagement of the selected gear set. For example, during an upshift, themechanical synchronizer utilizes frictional forces to decrease the rateof rotation of the driveshaft so that the desired gear of the driveshaftis engaged smoothly to drive the desired gear of the driven shaft.Conversely, during a downshift, the mechanical synchronizer increasesthe rate of rotation of the driveshaft so that the desired gear isengaged smoothly to drive the desired gear on the driven shaft.Typically, with a manual transmission, there is a delay period betweendisengagement of the currently engaged gear and the subsequentsynchronization and engagement of the desired transmission gear. Also,during this process, the clutch connection between the engine outputshaft and the transmission input shaft needs to be disengaged prior tothe gear shifting process and re-engaged upon synchronization.

Thus, it is an object of the present invention to provide anelectromechanical automatic transmission which utilizes the manual-typetransmission design in order to eliminate the parasitic lossesassociated with the torque converter and the hydraulic controls ofconventional automatic transmissions. The electromechanical automatictransmission of the present invention is essentially an automated manualtransmission. The design utilizes a dual clutch/dual input shaft layout.The layout is the equivalent of having two transmissions in one housing.Each transmission can be shifted and clutched independently.Uninterrupted power upshifting and downshifting between gears isavailable along with the high mechanical efficiency of a manualtransmission being available in an automatic transmission. Significantincreases in fuel economy and vehicle performance are achieved.

Two independently acting electromechanical shift actuators are providedwith barrel-shaped cam members to shift conventional manualsynchronizers with the clutches and blocker rings.

The dual clutch system consists of two dry discs driven by a commonflywheel assembly. Two electromechanical clutch actuators are providedto control disengagement of the two-clutch discs independently. Shiftsare accomplished by engaging the desired gear prior to a shift event andsubsequently engaging the corresponding clutch. The clutch actuatorshave assist springs to reduce the power needed to disengage theclutches. The actuators also have compensation mechanisms toautomatically adjust for clutch disc wear over the life of the clutchdiscs.

The transmission of the present invention can be in two different gearratios at once, but only one clutch will be engaged and transmittingpower. To shift to the new gear ratio, the driving clutch will bereleased and the released clutch will be engaged. The two-clutchactuators perform a quick and smooth shift as directed by an on-boardvehicle control system using closed-loop control reading engine RPMs ortorque. The transmission shaft that is disengaged will then be shiftedinto the next gear ratio in anticipation of the next shift.

A hill holder mechanism is provided in the form of an engagableoverrunning one-way roller clutch. This clutch will be engaged when thetransmission is in first, second, or third gears in order to preventvehicle rollback on a hill. A series of four synchronizer pairs arepreferably used on the two input shafts. The hill holder mechanism isselectively engaged by one of the synchronizers. The hill holderprevents rollback of the vehicle when it is stopped. Contrary to anautomatic transmission, there is no engine torque required to hold thevehicle from rolling back on a grade, thus efficiency is improved.

A lubrication system is provided such that a center plate is providedwithin the transmission housing for supporting an end of one of the twoinput shafts and also supports a lubrication pump mechanism which isdriven by a reverse idler gear also mounted to the center plate. Thelubrication pump mechanism draws lubrication fluid from the bottom ofthe transmission housing, through fluid passages in the center plate,and delivers the lubrication fluid to a center fluid passage disposedwithin the first input shaft. The center first input shaft, as well asthe hollow second input shaft, are provided with radial fluid passageswhich communicate lubrication to each of the gears mounted on each ofthe first and second input shafts. Efficiency is increased when the oillevel is below the geartrain, thus reducing parasitic drag (windageloss).

Further areas of applicability of the present invention will becomeapparent from the detailed description provided hereinafter. It shouldbe understood however that the detailed description and specificexamples, while indicating preferred embodiments of the invention, areintended for purposes of illustration only, since various changes andmodifications within the spirit and scope of the invention will becomeapparent to those skilled in the art from this detailed description.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will become more fully understood from thedetailed description and the accompanying drawings, wherein:

FIG. 1 is a sectional view of the electromechanical automatictransmission according to the principles of the present invention;

FIG. 2 is a detailed cross-sectional view of the dual cam assembly usedfor disengaging the dual clutch assemblies according to the principlesof the present invention;

FIG. 2A is an illustration of the 2-4-6, hill holder cam profile;

FIG. 2B is an illustration of the R-1-3-5 cam profile;

FIG. 3 is a side view of the R-1-3-5 side clutch actuator according tothe present invention;

FIG. 4 is a side view of the 2-4-6 hill holder side clutch actuatoraccording to the present invention;

FIG. 5 is an end view of the dual clutch assembly according to theprinciples of the present invention;

FIG. 6 is an end view of the clutch actuator assembly and dual camassembly according to the principles of the present invention with eachof the clutch actuator assemblies in the disengaged position;

FIG. 7 is an end view of the clutch actuator and dual cam assembly asshown in FIG. 6, with the right side clutch actuator in the disengagedposition;

FIG. 8 is an end view of the clutch actuator assembly and dual camassembly, with the right side clutch actuator in the adjust position;

FIG. 9 is an end view of the clutch actuator and dual cam assembly asshown in FIG. 6, with the left side clutch actuator in the disengagedposition;

FIG. 10 is an end view of the clutch actuator assembly and dual camassembly, with the left side clutch actuator in the adjust position;

FIG. 11 is a top view of the shift rail assembly according to theprinciples of the present invention;

FIG. 12 is a sectional view of the R-1-3-5 shift actuator according tothe principles of the present invention;

FIG. 13 is a sectional view of the 2-4-6-Hill Holder shift actuatoraccording to the principles of the present invention;

FIG. 14 is an illustration of the cam grooves provided in the 2-4-6-HillHolder shifter cam according to the principles of the present invention;

FIG. 15 is an illustration of the cam grooves of the R-1-3-5 shifter camaccording to the principles of the present invention;

FIG. 16 is an end view of the electromechanical automatic transmissionaccording to the principles of the present invention, with parts removedin order to illustrate the shift actuators, parking brake, and reverseidler gear/lube pump mechanism according to the principles of thepresent invention;

FIG. 17 is a plan view of the center plate with the parking sprag andreverse idler assembly mounted thereto;

FIG. 18 is a cross-sectional view of the center plate taken through thereverse idler gear/pump mechanism;

FIG. 19 is a plan view of the front side of the center plate,illustrating the lubrication passages provided therein for communicationbetween the geroter pump and the lubrication passage provided in thefirst input shaft;

FIG. 20 is a side view of the center plate shown in FIG. 19;

FIG. 21 is a top view of the center plate shown in FIG. 19; and

FIG. 22 is a schematic illustration of the control system for theelectromechanical automatic transmission according to the principles ofthe present invention.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

With reference to the accompanying drawings, the electromechanicalautomatic transmission 10, according to the principles of the presentinvention, will now be described. The electro-mechanical automatictransmission 10 is provided with a gear train 12 which includes a firstinput shaft 14 and a second hollow input shaft 16 which is concentricwith the first input shaft 14. Each of the input shafts 14, 16 support aplurality of rotatably mounted drive gears which are engaged withrespective driven gears mounted to a driven shaft 18. A first frictonclutch 20 is provided for transmitting torque from the engine outputshaft (not shown) to the first input shaft 14. A second friction clutch22 is provided for transmitting drive torque from the engine outputshaft to the second input shaft 16. A dual cam assembly 24, along withfirst and second clutch actuators 26, 28 (see FIGS. 3-4 and 6-10) areprovided for selectively disengaging the first and second frictionclutches 20, 22.

The gear train 12 includes a reverse 30, first 32, third 34, and fifth36 speed gears rotatably mounted to the first input shaft 14. Areverse-first synchronizer device 38 is provided for selectivelyengaging the reverse gear 30 and first speed gear 32 to the first inputshaft 14. A third-fifth synchronizer device 40 is provided forselectively engaging the third and fifth speed gears 34, 36 to the firstinput shaft 14. Second 42, fourth 44, and sixth 46 speed gears arerotatably mounted to the second input shaft 16. A second-fourthsynchronizer device 48 is provided for selectively engaging the secondand fourth speed gears, 42, 44, respectively to the second input shaft16. A sixth speed/hill holder synchronizer device 50 is provided forselectively engaging the sixth speed gear 46 to the second input shaft16. In addition, the sixth speed/hill holder synchronizer 50 alsoengages an overrunning one-way clutch (Hill Holder) device 52 forpreventing the vehicle from rolling backward down a hill.

The first input shaft 14 is supported by a bearing assembly 54. Bearingassembly 54 has an inner race 54a supported on the first input shaft 14and an outer race 54b supported on the second input shaft 16. The secondinput shaft 16 includes a two-piece construction with a first shaftportion 16A and a second shaft portion 16B, each fastened together by aplurality of fasteners and/or pins 53 generally in the vicinity of thebearing 54. In addition, a seal 55 is provided between the first shaftportion 16A of the second input shaft 16 and the first input shaft 14.At a second end, the first input shaft 14 is supported by a needlebearing assembly 60 disposed within a central hub portion of fifth speedgear 36. Fifth speed gear 36 is supported by the end plate 62 via abearing assembly 64. A center plate 66 is provided within the housing 58and is provided with an opening 68 through which the first and secondinput shafts 14, 16 extend. The second input shaft 16 is supportedwithin a front plate 56 of the transmission housing 58 via a bearingassembly 70 which is generally concentric with bearing 54. The drivenshaft 18 is supported at a front end by the front plate 56 via a bearingassembly 72 and at a rear end by the end plate 62 via a bearing assembly74. The driven shaft 18 is provided with a reverse driven gear 76, afirst speed driven gear 78, a second speed driven gear 80, a third speeddriven gear 82, a fourth speed driven gear 84, a fifth speed driven gear86, a sixth speed driven gear 88, and a parking gear 90. The drivenshaft 18 extends through an opening 92 in center plate 66 and issupported by needle bearing assembly 94.

The first input shaft 14 is drivingly engaged with the engine outputshaft via first clutch 20, while second input shaft 16 is engaged withthe engine output shaft via second clutch 22. The first and secondclutches 20, 22 include a flywheel assembly including a first flywheel96 which is mounted to the engine output shaft (not shown). A secondflywheel 98 is mounted to the first flywheel 96 for rotation therewith.The first clutch 20 includes a friction plate 100 disposed between thefirst flywheel 96 and a pressure plate 102. Pressure plate 102 is biasedby a belleville spring 104 into a normally engaged position. Thefriction plate 100 is engaged with a hub portion 106 which is mounted tothe first input shaft 14 via a spline connection. A torsion springsystem is provided between the friction plate and the hub 106, as iswell known in the art. A lever 110 engages the dual cam assembly 24 andis attached to linkage system 112 which is attached to the pressureplate 102 for disengaging the pressure plate 102 from the friction plate100 in order to disengage the first clutch 20 upon actuation of theclutch actuator 28 and dual cam assembly 24.

The second clutch 22 similarly includes a friction plate 116 which isdisposed between the second flywheel 98 and a pressure plate 118. Abelleville spring 120 is provided between the pressure plate 118 and aclutch cover plate 122. The second clutch 22 includes a hub 124 which isconnected to the second input shaft 16 by a spline connection. Thefriction plate 116 is connected to the hub 124 via a torsion springassembly 126, as is known in the art. A disengagement lever 128 engagesthe dual cam assembly 24 and is attached to a linkage assembly 130 andis operable in order to disengage the second clutch 22.

The first and second clutches 20, 22 are supported within a bell housing132 by the flywheel 96 along with the dual cam assembly 24 and clutchactuators 26, 28 which are supported by the bell housing 132. Theflywheel 96 is supported by the engine output shaft (not shown). Withreference to FIGS. 3 and 4, the clutch actuators 26 and 28 will now bedescribed. It should be understood that the left and right side clutchactuators 26, 28 are virtually identical in their construction.Accordingly, a single description with respect to the right and leftside clutch actuators 26, 28 will be provided wherein like referencenumerals designate common elements. The clutch actuators 26, 28 includean electric motor 134 which drives a planetary reduction gear assembly136. The planetary reduction gear assembly 136 is provided with asplined output shaft which engages a corresponding splined shaft 138. Apawl teeter arm 140 is mounted to the splined shaft 138 for rotationtherewith. A pivot pin 142 is provided in the end of the pawl teeter arm140. A pawl teeter assembly 144 is mounted to the pivot pin 142 and isprovided with a pawl 146 at one end thereof and a roller 148 at a secondend thereof, as best seen in FIGS. 7-10. The pawl 146 engages anadjuster plate 150 which is provided with a semi-circular radialoutermost surface having a plurality of teeth provided therein. Theadjuster plate 150 is mounted to a hub portion 152 of a pivot arm 154.The pivot arm 154 of the right and left side clutch actuators 26, 28 areeach attached to a link 156 which is attached to a cam retainer lever158, 160 of the dual cam assembly 24, as shown in FIGS. 6-10. The pivotarm 154 is provided with a shaft extension 162 which is connected to apotentiometer 164 which measures the position of the pivot arm 154.

As mentioned above, the pivot arms 154 of the right and left side clutchactuators 26, 28 are attached to links 156 which are in turn connectedto cam retainer levers 158, 160 of dual cam assembly 24. With referenceto FIG. 2, the dual cam assembly 24 will be described in greater detail.The dual cam assembly 24 is provided with a clutch ramp hub 170 which isprovided with a flange portion 172 which mounts to the front plate 56and a cylindrical body portion 174. The 2-4-6 cam retainer lever 160 isrotatably mounted to the cylindrical body portion 174 of clutch ramp hub170 via a bearing assembly 176. The cam retainer lever 160 includes aring-shaped body portion 178 and a lever arm portion 180 extendingradially therefrom. The ring portion 178 of cam retainer lever 160supports a plurality of cam rollers 182 along annular groove 184. A camring 186 is provided with a plurality of axially extending cam surfaces188 which engage the cam rollers 184. FIG. 2A provides an illustrationof the profile of the cam surfaces 188 of the cam ring 186. In thisembodiment, the profile includes three cam surfaces 188 which eachcorrespond to a cam roller 182. The cam ring 186 is slidably connectedto the clutch ramp hub 170 by axial splines 187, wherein the rotation ofcam retainer lever 160 relative to cam ring 186 causes the cam ring 186to move axially relative to the clutch ramp hub 170 as the cam rollers182 traverse against the sloped cam surfaces 188.

The R-1-3-5 cam retainer lever 158 includes a ring shaped body portion189 and a lever arm portion 190 extending radially therefrom. The ringshaped body portion 189 is provided with a bearing assembly 191 on theradial surface of the 2-4-6 cam retainer lever 160 so that the camretainer lever 158 can rotate relative to the cam retainer lever 160.The cam retainer lever 158 also supports a plurality of cam rollers 182'along annular groove 184'. Each cam roller 182' corresponds with asloped cam surface 188'of an outer cam ring 192. FIG. 2B provides anillustration of the profile of the cam surfaces 188' of the outer camring 192. In this embodiment, the profile includes three cam surfaces188' which each correspond to a cam roller 182'. The outer cam ring 192is splined to the inner cam ring 186 at 193 and is capable of movingaxially relative thereto. Upon rotation of the cam retainer lever 158,the cam surfaces 188' move in engagement with cam rollers 182' to causethe outer cam ring 192 to move axially relative to the clutch ramp hub170. The inner cam ring 186 and outer cam ring 192 are each providedwith a cam release pad 194, 194' which is rotatably supported by theinner and outer cam rings 186, 192, respectively, via a bearing assembly196, 196'. An O ring retainer 198, 198' and a retaining ring 200, 200'are provided for retaining the cam release pads 194, 194'in positionrelative to the inner and outer cam rings 186, 192. With reference toFIG. 1, the lever 110 of first clutch 20 and lever 128 of second clutch22 each include an end portion which engage the cam release pads 194,194' of the dual cam assembly 24. Accordingly, by rotation of camretainer levers 158, 160 causing axial movement of cam release pads 194,194', selective disengagement of the first and second clutch assemblies20, 22 can be obtained.

With reference to FIGS. 6-10, the operation of the clutch actuators forengaging the first and second clutches 20, 22 will be described. Asshown in FIG. 6, each of the clutch actuators 26, 28 are shown in thedisengaged position. Each clutch actuator 26, 28 is provided with anassist spring 202 which is adjustably mounted at a first end to the bellhousing 132 by a ball socket joint 204 and which is connected at asecond end to an assist arm 206 which extends from the pawl teeter arm140, as best shown in FIGS. 7-10. The assist springs 202 can be adjustedvia a spring adjustment device 216 which can include, for example, athreaded adjustment apparatus for continuously variable adjustment ofthe compression amount of the assist spring 202. The pawl teeter arm 140is also provided with a switch activation arm 208 which engages a switch210 which shuts off the electric motor 134 of the actuators 26, 28. Theassist spring 202 is designed so as to provide an increasing assistforce as the pawl teeter arm 140 is rotated from the engaged to thedisengaged positions. In other words, as shown in FIG. 7, the springforce of the assist spring 202 acts through the axis of rotation of thepawl teeter arm 140. As the electric motor 134 drives the pawl teeterarm 140, the moment arm upon which the assist spring 202 acts upon thepawl teeter arm 140 increases with the rotation of the pawl teeter arm140. This can best be seen in FIG. 6 wherein the pawl teeter arm 140 inthe disengaged position is rotated so that the assist spring 202 acts ona large moment arm X in order to provide a large assist force. The needfor the increasing assist force is due to the increasing spring force ofthe belleville springs 104 and 120 which bias the pressure plates 102and 118 of first and second clutches 20, 22, respectively, into thenormally engaged position. Accordingly, as the pressure plates 102, 118are moved away from the engaged position, the force of the bellevillesprings 104, 120 increases. Thus, in order to consistently reduce therequired motor force for disengaging the clutches 20, 22, the assistspring 202 and increasing moment arm arrangement of the presentinvention provides a consistently increasing assist force.

Upon rotation of the pawl teeter arm 140, the pawl 146 of the pawlteeter assembly 144 transmits torque to the adjuster plate 150 and pivotarm 154 which is mounted for rotation therewith. When the clutchactuators 26, 28 are in the normally engaged position such as shown inFIGS. 7 and 9, respectively, the switch activation arm 208 rests againstthe switch 210 and the roller 148 of pawl teeter assembly 144 restsagainst the stop surface 212.

As the clutch discs wear down, the clutch actuators 26, 28 are providedwith an automatic adjustment feature wherein as the roller 148 of pawlteeter assembly 144 rests against the stop surface 212, the pawl 146 isallowed to disengage from the serrated teeth of the adjuster plate 150so that the adjuster plate 150 is free to move relative to the pawlteeter assembly 144. Preload springs 213 are provided to apply a tensionforce between the adjuster plate 150 and the pawl teeter arm 140 inorder to preload the adjuster plate 150 and thus bring the dual camassembly to the fully engaged position. Accordingly, as the clutch diskswear down, the adjuster plates 150 rotate further as biased by thepreload spring 213 during the adjustment in order for the clutch tobecome fully engaged. Upon subsequent activation of the clutch actuator,the pawl 146 will reengage with the adjuster plate 150 and the clutchactuator is automatically adjusted to compensate for wear of the clutchdisks. Thus, clutch clamp load and torque capacity are maintained. Theclutch actuators 26, 28 are mounted to the housing 132 by clutchactuator mounts 214. It should be readily understood to one of ordinaryskill in the art that the operation of the left and right clutchactuators 26, 28 is identical and that further description with respectto the left and right clutch actuators 26, 28 is unnecessary in view ofthis similarity of operation.

The shift actuators 218, 219, according to the present invention willnow be described with reference to FIGS. 11-16. The electromechanicalautomatic transmission 10, according to the present invention, isprovided with a first shift rail 220 and a second shift rail 222 eachprovided with a shift lug 224 securely fastened to the shift rails andeach having a cam roller 226 (as shown in FIG. 12) which operativelyengage cam grooves 228 provided in a barrel-shaped shifter cam 230 ofthe R-1-3-5 shift actuator 218. The configuration of the cam grooves 228for the R-1-3-5 shift actuator 218 is shown in FIG. 15. As shown in FIG.12, the R-1-3-5 shift actuator 218 includes an electric motor 234 whichdrives a planetary reduction gear assembly 236. The planetary reductiongear assembly 236 drives a shaft 238 which is connected to the shiftercam 230 by a keyway 240. The shifter cam 230 is provided within ahousing 242 and is supported by a pair of bearings 244. A potentiometer246 is provided for measuring the position of the shifter cam 230. Thepotentiometer 246 is connected to the shaft 238 by a coupler 248 whichis disposed within a housing extension 250. The shifter cam 230, uponrotation, drives shift lugs 224 mounted on first and second shift rails220, 222 for selectively moving the shift rails and thus the shift forks252, 254 mounted to the shift rails 220, 222, respectively, as shown inFIG. 11. The shift fork 252 is associated with the reverse-first gearsynchronizer device 38. The shift fork 254 is associated with thethird-fifth gear synchronizer 40.

The electromechanical automatic transmission is also provided with thirdand fourth shift rails 256, 258, respectively, which are each providedwith a shift lug 224 securely mounted to each shift rail 256, 258. Eachshift lug 224 includes a cam roller 226 which operatively engage camgrooves 260 provided in the shifter cam 262 of shift actuator 219, asshown in FIG. 13. The cam grooves 260 for the shift actuator 219 areshown in FIG. 14. A 2-4 shift fork 263 is mounted on the shift rail 256for actuating the second-fourth speed synchronizer 48. A sixthHillHolder shift fork 264 is mounted to the shift rail 258 for selectivelyengaging the sixth-Hill Holder synchronizer 50. With reference to FIG.13, the 2-4-6 shift actuator 219 has substantially the same constructionas the R-1-3-5 shift actuator 218 shown in FIG. 12.

With reference to FIGS. 1 and 17-21, the lubrication system of thepresent invention will be described. The lubrication system includes agerotor pump 272 (best shown in FIGS. 18 and 19) mounted to the centerplate 66 and driven by the reverse idler gear 274. The reverse idlergear 274 is mounted to the center plate 66 by a mount bracket 276 whichis mounted to the center plate 66 by a pair of fasteners 278, as shownin FIG. 17. The reverse idler gear 274 is engaged with the reverse drivegear 30 and reverse driven gear 76. The reverse idler gear 274 isprovided with a center shaft 304 which is mounted to the mount bracket276 and is provided with bearing assemblies 306 for supporting thecenter shaft 304. The gerotor pump 272 is attached to the center shaft304 and is provided within a pump chamber 279 and is provided with acover 280. An oil passage 282 is provided in communication with thegerotor pump 272 and receives oil from an oil pick-up tube 284, as shownin FIG. 17. A second oil passage 286 is in communication with the outletof the gerotor pump 272 and a lubrication groove 288 which communicateslubrication fluid to a lubrication passage 290 in the first input shaft14. The first input shaft 14 is provided with radial passages 290a-290gwhich communicate with the lubrication passage 290 for providinglubrication to the reverse gear 30 and first through sixth gears 32, 42,34, 44, 36, 46.

A parking sprag 294 is provided for engaging the parking gear 90provided on the driven shaft 18. The parking sprag 294 is mounted to thecenter plate 66 by a mount boss 296. The parking sprag 294 is attachedto a rod assembly 298 which is attached to a parking lever engagementassembly 300. The center plate 66 is provided with a plurality ofmounting holes 301 for receiving threaded fasteners 302 for mounting thecenter plate 66 to the housing 58.

With reference to FIG. 22, a transmission controller 320 is provided foroperating the clutch actuators 26, 28 and the shift actuators 218, 219.The transmission controller 320 provides signals to the driver motors134 of the clutch actuators 26, 28 as well as to the driver motors 234of the shift actuators 218, 219. The transmission controller 320 alsomonitors the position of the clutch actuators 26, 28 as well as theshift actuators 218, 219 via potentiometers 164, 246, respectively.Uninterrupted power shifting between gears is accomplished by engagingthe desired gear prior to a shift event. The transmission 10 of thepresent invention can be in two different gear ratios at once, with onlyone clutch 20, 22 being engaged for transmitting power. In order toshift to a new gear ratio, the current driving clutch will be releasedvia the corresponding clutch actuator and the released clutch will beengaged via the corresponding clutch actuator. The two clutch actuatorsperform a quick and smooth shift as directed by the transmissioncontroller 320 which monitors the speed of the input shafts 14 and 16via speed sensors 322 and 324, respectively, as well as the speed of thedriven shaft 18 via a speed sensor 326. Alternatively, the controller320 can determine the speed of the input shafts 14 and 16 based upon theknown gear ratio and the speed of the driven shaft 18 as detected bysensor 326. An engine speed sensor 327 is also provided and detects thespeed of the flywheel 96. Based upon the accelerator pedal position asdetected by sensor 328, the vehicle speed, and the current gear ratio,the transmission controller 320 anticipates the next gear ratio of thenext shift and drives the shift actuators 218, 219, accordingly, inorder to engage the next gear ratio while the corresponding clutchactuator is in the disengaged position. As a gear is engaged, thecorresponding input shaft which is disengaged from the engine outputshaft, becomes synchronized with the rotational speed of the drivenshaft 18. At this time, the clutch which is associated with the currentdriving input shaft is disengaged and the other clutch is engaged inorder to drive the input shaft associated with the selected gear.

The Hill Holder mechanism 52 is selectively engaged when thetransmission is in first, second, or third gears in order to preventvehicle rollback on a hill when the vehicle is at rest. Accordingly, thetransmission controller 320 determines when the vehicle operatingparameters are such that the Hill Holder feature is desirable.

The invention being thus described, it will be obvious that the same maybe varied in many ways. Such variations are not to be regarded as adeparture from the spirit and scope of the invention, and all suchmodifications as would be obvious to one skilled in the art are intendedto be included within the scope of the following claims.

What is claimed is:
 1. A transmission for use with a vehicle,comprising:a housing having a partition plate in a center portionthereof; a first drive shaft supported within said housing and having aplurality of drive gears rotatably mounted thereon for selectiveengagement with said first drive shaft, said first drive shaft extendingthrough said partition plate; a second drive shaft concentric with saidfirst drive shaft and having a plurality of drive gears rotatablemounted thereon for selective engagement with said second drive shaft; adriven shaft supported within said housing in parallel to said first andsecond drive shafts and including a plurality of driven gears fixedlymounted to said driven shaft in meshing engagement with correspondingones of said drive gears mounted to said first and second drive shafts;and a pump mechanism mounted on said partition plate for drawinglubrication fluid from a bottom of said housing and into a centrallylocated lubrication passage in said first drive shaft, wherein said pumpmechanism is driven by a reverse idler gear mounted to said partitionplate.
 2. The transmission according to claim 1 wherein said reverseidler gear is engaged with a reverse drive gear and a reverse drivengear.
 3. The transmission according to claim 1 wherein said reverseidler gear is mounted upon a center shaft which is provided with bearingassemblies for supporting said center shaft in said housing.
 4. Alubrication system for a transmission, comprising:a transmission housingincluding a partition plate including a pump chamber and inlet andoutlet fluid passages communicating with said pump chamber; and a pumpmechanism mounted in said pump chamber; and a reverse idler gear mountedto said partition plate and in driving engagement with said pumpmechanism.
 5. The lubrication system according to claim 4, wherein saidpartition plate supports an input shaft of the transmission such thatthe outlet fluid passage is in communication with the input shaft forsupplying lubrication to a central passage in said input shaft.